EP0041831A1 - Vorrichtung zur Luftzufuhr in dem Auspuffkrümmer einer Brennkraftmaschine - Google Patents

Vorrichtung zur Luftzufuhr in dem Auspuffkrümmer einer Brennkraftmaschine Download PDF

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Publication number
EP0041831A1
EP0041831A1 EP81302475A EP81302475A EP0041831A1 EP 0041831 A1 EP0041831 A1 EP 0041831A1 EP 81302475 A EP81302475 A EP 81302475A EP 81302475 A EP81302475 A EP 81302475A EP 0041831 A1 EP0041831 A1 EP 0041831A1
Authority
EP
European Patent Office
Prior art keywords
valve seat
valve
diameter
tube
chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP81302475A
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English (en)
French (fr)
Other versions
EP0041831B1 (de
Inventor
George Frank Hare
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
PULSE AIR RESEARCH LIMITED
Original Assignee
Pulse Air Research Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Pulse Air Research Ltd filed Critical Pulse Air Research Ltd
Priority to AT81302475T priority Critical patent/ATE39544T1/de
Publication of EP0041831A1 publication Critical patent/EP0041831A1/de
Application granted granted Critical
Publication of EP0041831B1 publication Critical patent/EP0041831B1/de
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
    • F01N3/08—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous
    • F01N3/10—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust
    • F01N3/24—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by constructional aspects of converting apparatus
    • F01N3/30—Arrangements for supply of additional air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/14—Silencing apparatus characterised by method of silencing by adding air to exhaust gases
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • This invention relates to devices for admitting air to the exhaust manifolds of internal combustion engines. Such devices may, for convenience, be referred to as "exhaust aspirators”.
  • an exhaust aspirator is to permit the induction of air into the exhaust manifold from the atmosphere at certain points during the cycle of pressure changes which occur in the exhaust manifold during normal running of the engine.
  • a function of an exhaust aspirator is to permit the induction of relatively clean air into the exhaust manifold so as to damp down such vacuum waves, thereby promoting more effective exhaust gas discharge. Also, the aspirator operates to cause the aspirated air, rather than exhaust gas to be drawn into a combustion chamber of the engine together with the combustion charge, in the manner mentioned above.
  • An object of the present invention is to provide an exhaust aspirator and a valve seat member therefor providing improved performance at engine speeds of one thousand five hundred r.p.m. and above.
  • a device for admitting air to the exhaust manifold of an internal combustion engine comprising:
  • the invention also provides a valve seat member suitable for use in a device as defined in the preceding paragraph.
  • the chamber defined by the valve disc and the valve seat member is of greater cross-sectional area in the region of the valve seat than at the closed end of the valve seat member.
  • the chamber may be formed with two cylindrical portions of differing diameters, for this purpose.
  • the diameter of the portion having the smaller diameter may be from 70% to 90% of the diameter of the portion having the larger diameter.
  • the air inlet opening may be of circular cross-sectional shape with a diameter lying within the range of 10% to 30% of the diameter of the cylindrical chamber portion of larger diameter.
  • the depth of the chamber measured from the valve seat to the closed end of the valve seat member may lie in the range of from 40% to 60% of the diameter of the cylindrical chamber portion of larger diameter.
  • Exhaust aspirator 10 comprises an air admission tube 12, a connector 14 at one end of the tube whereby the tube can be connected to the exhaust manifold (not shown) of an internal combustion engine, and a control valve assembly 16 at the other end of the air admission tube, to control the passage of gas through that tube. It is deemed unnecessary to describe or illustrate the exhaust manifold in detail since such a structure is so well known in the art.
  • Connector 14 is in the form of a steel tube 18 having screw-threaded end portions 20, 22 between which a central portion 24 carries six integrally-formed cooling fins 26.
  • Screw-threaded end portion 20 is to be received in an appropriately-drilled and tapped hole formed in the exhaust manifold of an internal combustion engine, such as a petrol engine of a car.
  • the hole to receive end portion 20 is preferably formed in the manifold as close as possible to the cylinder block of the engine. It may be formed in any one of the portions of the manifold connected to individual cylinders of the internal combustion engine.
  • Air admission tube 12 has a flanged inner end 28 which co-operates with a brass nut 30 to join tube 12 to connector 14.
  • the exhaust aspirator 10 shown in Fig 1 is intended for a car having a petrol engine, and air admission tube is of length 45cm.
  • the tube comprises inner, central and outer portions 32, 34 and 36 respectively, each of which is of constant internal diameter, the internal diameter of portion 36 being larger than that of portion 34, which in turn is larger than that of portion 32.
  • the three tube portions 32, 34 and 36 are formed of copper suitably brazed or welded together.
  • a stay 38 having an internal rubber grommet 40 is provided to receive through an aperture 42 a bolt (not shown) whereby the stay is secured to an appropriate fixed structure within the engine compartment of the car so as to reduce vibration of air admission tube 12 during use.
  • Control valve assembly 16 is formed predominantly of aluminium or of a metal alloy so as to have a density less than that of steel whereby vibration of the copper air admission tube 12 is reduced during use.
  • valve assembly 16 comprises interfitting inner and outer caps 44 and 46 respectively which form a housing for a valve seat member 4 H , a valve disc 50 to engage the valve seat, and a valve spring 52 to press the valve disc towards the valve seat.
  • Inner cap 44 has a central opening at its inner end in which is secured a tubular union 5 4 having.an internal screw thread 56 at its inner end in which is received a corresponding screw-threaded male union 58 provided at the outer end of air admission tube 12.
  • the outer end 60 of union 54 is in the form of a cylindrical sleeve forming a mounting for valve seat member 48 and a housing for valve disc 50 and valve spring 52.
  • outer cap 46 is proportioned to fit.over inner cap 44 to define a housing, and has deformable ears 62 which are bent over so as to secure the two caps together during assembly.
  • a gap for the entry of air into the control valve assembly 16 in the direction indicated by arrows 64 is provided between the two caps 44, 46.
  • valve seat member 48 is generally cup-shaped and is mounted with its open end 65 facing the air admission tube 12 and is formed with an air inlet opening 6b in its closed end 68.
  • the valve seat member provides an annular valve seat 70 at its open end.
  • the valve seat is flat and annular in form and provided with a very finely machined and polished surface for good sealing engagement with valve disc 50.
  • Valve seat member 48 is, on assembly, press-fitted into sleeve 60 so as to be gripped and held thereby.
  • Valve spring 52 is located at its inner end in a recess 72 formed in union 54, the spring pressing valve disc 50 against valve seat 70.
  • control valve assembly 16 is set so as to open (ie. valve disc 50 lifts from valve seat 70) upon application to air admission tube 12 of a pressure of from 10.2 cm. (4.0 inches) to 25.4cm. ( 1 0.0 inches) of water below one atmosphere.
  • the preferred range of pressures is from 11.5 cm to 21.5 cm of water below one atmosphere.
  • the setting which suits the majority of petrol engines for cars is 15.9 cm (6.25 inches) of water below one atmosphere, and variations of 0.6cm of water on both sides of this figure.
  • valve opening pressures are determined by means of a water manometer which is connected to tube 12 during assembly.
  • the valve opening pressure is set by adjustment of the position of valve seat member 48 in sleeve 6U during the operation of pressing valve member 48 into sleeve 60 as a friction-fit therein.
  • the vacuum which the valve assembly can sustain increases.
  • the correct position of the valve seat member is indicated when the valve assembly opens at the selected pressure in the ranges indicated above.
  • Valve disc 50 and valve seat member 48 define a chamber 74 on the atmospheric side of the valve disc (ie. the opposite side from the exhaust manifold) into which chamber air can be drawn through air inlet opening 66.
  • valve seat member 48 itself is cylindrical and the chamber 74 formed within it is likewise cylindrical and has a uniform diameter of 10mm.
  • Air inlet opening 66 is likewise 'cylindrical in form, its diameter is 2mm and it has frusto- conical portions at its opposite ends.
  • the depth 7 b of the chamber 74 is 5mm measured between valve seat 70 and the closed end of chamber 74.
  • Valve seat 78 shown in Fig 4 differs from valve seat 48 in having a chamber 80 which is of greater cross-sectional area in the region of the valve seat 82 than at the closed end 84 of the valve seat member. This is achieved by forming chamber 80 with inner and outer portions 86 and 88 respectively, of differing diameters.
  • the smaller diameter inner chamber portion 86 is of diameter 8mm and the outer chamber portion 88 is of the same diameter as chamber 74 namely 10mm.
  • Air inlet 90 is of diameter 2mm - the same as inlet 66.
  • chambers 74 and 80 are critical to the performance of the exhaust aspirator at higher engine speeds. It has also been found that the diameter 92 of chamber portion 86 should be from 70% to 90% of the diameter 94 of the chamber portion 88.
  • the diameter of air inlet opening 90 has been found preferably to lie in the range of 10% to 30% of the diameter of portion.88 of chamber 80 -.the figure in this embodiment being 20%.
  • the depth 96 of chamber 80 measured from valve seat 82 to the closed end 84 of the valve seat member should preferably lie in the range from 40% to 60% of the diameter of chamber portion 88 - the depth in this embodiment being 5mm which is 50% of the diameter of the wider chamber portion.
  • Valve disc 50 is formed of a metal of density lower than that of steel - preferably of a very low density alloy material.
  • the disc is flat, formed.with a very highly polished surface for engagement with valve seat 70, and lightly pressed against the seat by coiled compression spring 52.
  • the passage of exhaust gases from a combustion chamber of an engine through an exhaust manifold to the exhaust outlet proceeds in a series of high pressure waves, each followed by a corresponding vacuum wave which reduces pressure within air admission tube 12 sufficiently to lift valve disc 50 from its valve seat and to admit air to tube 12 through the air inlet opening .in the valve seat member 48 or 78.
  • Successive engine cycles and the assoicated vacuum waves produce an inflow of air to the exhaust manifold - thereby reducing the re-cycling of exhaust gases in the engine, damping the vacuum waves and promoting more effective exhaust gas discharge.
  • valve seat member 78 With the valve seat member 78, engine speeds of up to seven thousand revolutions per minute can be accommodated with satisfactory opening of the valve.
  • chamber 80 of the step in diameter between chamber portions 88 and 86 provides frequency compatability between the two sides of valve disc 5 0 . It . is believed that resonance factors enter into the improvement in performance of the embodiments of the invention described above, as compared with previously proposed devices. These effects avoid the build up of static waves during use and thus avoid the effective blanking-off of the air admission valve at relatively low engine speeds.
  • chamber 80 By designing chamber 80 so that its volume and dimensions, and indeed its shape, are conducive to resonant frequency compatability with the air admission tube 1 2 and the exhaust system of the engine, an improvement in the response of the valve assembly at higher engine speeds is achieved.
  • the need for frequency compatability between the ducts and chambers on the opposite sides of a control valve of an exhaust aspirator is believed to be a design criterion which is entirely new in this art.
  • the resonant frequency of the chamber 80 need not be the same frequency as that of the air admission tube - it is sufficient for the former to be a harmonic of the latter.
  • FIG. 5 The embodiment of Figure 5 is constructed in a similar manner to that of the embodiment of Figures 1 to 3, and cap 44, valve seat member 48, valve disc 50, and valve spring 52 are constructed as described above and have the same reference numerals as in the previous embodiment.
  • a union 100 (corresponding to union 54) is formed with a lower internally screw-threaded portion 102 and an upper portion 104 - the latter corresponding to portion 60 in the previous embodiment.
  • Union 100 is secured to cap 44 as in the previous embodiment, and valve seat member 48 is secured within portion 104 with valve spring 52 holding valve disc 50 against the valve seat generally as described above.
  • a screw-threaded adjustment sleeve 106 is received in portion 102 of the union and supports an annular washer 108 which is a free sliding fit within portion 102 of the union and serves as a seat for the inner end of valve spring 52.
  • Position-adjustment of member 1U6 by rotating it by means of a hexagon head 110 adjusts the vacuum at which valve disc 50 opens.
  • a lock nut 112 enables a desired setting of member 1U6 to be maintained.
  • This embodiment of the invention enables determinations to be made of the optimum valve opening pressure for any particular engine. Adjustments of the valve spring pressure can be made in situ-on the engine. The optimum setting is indicated by the maximum flow rate of air through the valve assembly of Figure 5. This may be determined by means of a sensitive pressure monitoring device connected thereto - for example an altimeter.
  • valve opening pressure is pre-set during manufacture.
  • Figure 5 also illustrates two further modifications: the provision of a larger diameter portion 114 within valve member 48 (as in Fig 4), and the provision within the valve member 48 of a chamber of generally conical form as indicated by broken lines 116, the conical chamber tapering towards the air inlet opening 118. This modification is believed to provide improved resonance characteristics for certain applications.
  • valve assembly may be achieved by use of washers 108 having internal openings 120 of various diameters - whereby the resonant frequency of the chamber on the engine side of valve 50 may be changed.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Health & Medical Sciences (AREA)
  • Toxicology (AREA)
  • Safety Valves (AREA)
  • Fluid-Driven Valves (AREA)
  • Exhaust Silencers (AREA)
  • Exhaust Gas After Treatment (AREA)
EP81302475A 1980-06-06 1981-06-04 Vorrichtung zur Luftzufuhr in dem Auspuffkrümmer einer Brennkraftmaschine Expired EP0041831B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT81302475T ATE39544T1 (de) 1980-06-06 1981-06-04 Vorrichtung zur luftzufuhr in dem auspuffkruemmer einer brennkraftmaschine.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB8018661 1980-06-06
GB8018661 1980-06-06

Publications (2)

Publication Number Publication Date
EP0041831A1 true EP0041831A1 (de) 1981-12-16
EP0041831B1 EP0041831B1 (de) 1988-12-28

Family

ID=10513884

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EP81302475A Expired EP0041831B1 (de) 1980-06-06 1981-06-04 Vorrichtung zur Luftzufuhr in dem Auspuffkrümmer einer Brennkraftmaschine

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EP (1) EP0041831B1 (de)
AT (1) ATE39544T1 (de)
DE (1) DE3176630D1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0492240A1 (de) * 1990-12-28 1992-07-01 Firma J. Eberspächer Vorrichtung zum Verbessern der Schalldämpfbarkeit eines Verbrennungsmotor-Abgasstroms
WO1997025526A1 (en) * 1996-01-12 1997-07-17 Gentech Design Limited Exhaust manifold device
GB2368371A (en) * 2000-10-28 2002-05-01 Ribbit Ltd Method of operating an i.c. engine with addition of secondary air into the exhaust and production of reformed fuel by mechanical action

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB639790A (en) * 1941-12-05 1950-07-05 Luxe Products Corp De Improvements in or relating to the exhaust manifolds of multi-cylinder internal combustion engines
GB655761A (en) * 1944-10-21 1951-08-01 Luxe Products Corp De Improved means for admitting air to the exhaust manifolds of internal combustion engines
US3253401A (en) * 1964-06-08 1966-05-31 Wells Carter Exhaust aid device
US3390520A (en) * 1967-08-04 1968-07-02 Exhaust Controls Inc Air supplying device for internalcombustion engines
US3455106A (en) * 1967-05-05 1969-07-15 Charles R Flint Exhaust manifold device
FR2108327A5 (de) * 1970-09-22 1972-05-19 Alfa Romeo Spa
DE2337051A1 (de) * 1973-07-20 1974-02-14 Nippon Denso Co Sekundaerluftzufuhrsystem fuer brennkraftmaschinen
US3871175A (en) * 1972-07-28 1975-03-18 Nippon Denso Co Secondary air supply system for an internal combustion engine

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB639790A (en) * 1941-12-05 1950-07-05 Luxe Products Corp De Improvements in or relating to the exhaust manifolds of multi-cylinder internal combustion engines
GB655761A (en) * 1944-10-21 1951-08-01 Luxe Products Corp De Improved means for admitting air to the exhaust manifolds of internal combustion engines
US3253401A (en) * 1964-06-08 1966-05-31 Wells Carter Exhaust aid device
US3455106A (en) * 1967-05-05 1969-07-15 Charles R Flint Exhaust manifold device
US3390520A (en) * 1967-08-04 1968-07-02 Exhaust Controls Inc Air supplying device for internalcombustion engines
FR2108327A5 (de) * 1970-09-22 1972-05-19 Alfa Romeo Spa
GB1368286A (en) * 1970-09-22 1974-09-25 Alfa Romeo Spa Exhaust system for internal combustion engines
US3871175A (en) * 1972-07-28 1975-03-18 Nippon Denso Co Secondary air supply system for an internal combustion engine
DE2337051A1 (de) * 1973-07-20 1974-02-14 Nippon Denso Co Sekundaerluftzufuhrsystem fuer brennkraftmaschinen

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0492240A1 (de) * 1990-12-28 1992-07-01 Firma J. Eberspächer Vorrichtung zum Verbessern der Schalldämpfbarkeit eines Verbrennungsmotor-Abgasstroms
WO1997025526A1 (en) * 1996-01-12 1997-07-17 Gentech Design Limited Exhaust manifold device
AU707029B2 (en) * 1996-01-12 1999-07-01 Gentech Design Limited Exhaust manifold device
US6119454A (en) * 1996-01-12 2000-09-19 Gentech Design Limited Exhaust manifold device
GB2368371A (en) * 2000-10-28 2002-05-01 Ribbit Ltd Method of operating an i.c. engine with addition of secondary air into the exhaust and production of reformed fuel by mechanical action
WO2002035078A1 (en) 2000-10-28 2002-05-02 Ribbit Limited Method of operating a combustion apparatus
GB2368371B (en) * 2000-10-28 2004-05-12 Ribbit Ltd Method of operating an engine
US6769244B2 (en) 2000-10-28 2004-08-03 Ribbit Limited Method of operating a combustion apparatus

Also Published As

Publication number Publication date
DE3176630D1 (en) 1989-02-02
ATE39544T1 (de) 1989-01-15
EP0041831B1 (de) 1988-12-28

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